EP3807559B1 - Joint mécanique avec joint secondaire haute température et haute pression - Google Patents

Joint mécanique avec joint secondaire haute température et haute pression Download PDF

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Publication number
EP3807559B1
EP3807559B1 EP19819368.2A EP19819368A EP3807559B1 EP 3807559 B1 EP3807559 B1 EP 3807559B1 EP 19819368 A EP19819368 A EP 19819368A EP 3807559 B1 EP3807559 B1 EP 3807559B1
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EP
European Patent Office
Prior art keywords
seal
sealing gasket
sealing
backing plate
sealing surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19819368.2A
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German (de)
English (en)
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EP3807559A4 (fr
EP3807559A1 (fr
Inventor
Eric Hamilton
Daniel Nelson
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Flowserve Management Co
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Flowserve Management Co
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Publication of EP3807559A4 publication Critical patent/EP3807559A4/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3436—Pressing means
    • F16J15/3448—Pressing means the pressing force resulting from fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/38—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member sealed by a packing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3228—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip formed by deforming a flat ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3436—Pressing means
    • F16J15/344—Pressing means the pressing force being applied by means of an elastic ring supporting the slip-ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3464—Mounting of the seal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/36—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member connected by a diaphragm or bellow to the other member
    • F16J15/363—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member connected by a diaphragm or bellow to the other member the diaphragm or bellow being made of metal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3436—Pressing means
    • F16J15/3452—Pressing means the pressing force resulting from the action of a spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/34—Sealings between relatively-moving surfaces with slip-ring pressed against a more or less radial face on one member
    • F16J15/3464—Mounting of the seal
    • F16J15/3472—Means for centering or aligning the contacting faces

Definitions

  • the invention relates to rotating shaft seals, and more particularly, to rotating shaft mechanical seals.
  • a mechanical seal is a seal that is formed by close proximity of two flat, annular, non-contacting seal faces, usually referred to as a static seal face and a rotating seal face, in that one face is typically static and sealed to a housing, while the other face is sealed to a rotating shaft and rotates with the shaft.
  • the two seal faces are annular, and coaxial with the rotating shaft, whereby the long axis of the shaft is also the common axis of the annular seal faces.
  • Document US-B-9394799 for example describes an air riding seal for a turbine and having the features of the preamble of claim 1.
  • the two seal faces are lapped flat to a very high degree of flatness, which allows the faces to be configured in a parallel relationship whereby they are not physically in contact with each other, but are separated by a gap that can be as narrow as one micron or less.
  • the gap itself is also annular in shape, and shares a common central axis with the two annular seal faces, and with the rotating shaft.
  • the configuration of a mechanical seal is such that, if each of the annular seal faces were considered to lie in a plane, then the planes of the annular seal faces would be parallel to each other, and both would be perpendicular to the central axis of the rotating shaft.
  • the gap between the seal faces in a mechanical seal is filled with a film formed by fluid that is radially forced into the gap from either or both of the inner and outer boundaries of the gap due to differential pressure between the inner and outer boundaries.
  • the film serves to lubricate the gap, and to maintain the separation of the faces so that they do not mechanically wear against each other. Often, but not always, this lubricating fluid is process fluid. It is inherent to mechanical seals that during operation a very small amount of the lubricating fluid leaks radially across the gap, i.e. from the inner boundary of the annular gap to the outer boundary of the gap, and/or vice versa. The amount of leakage varies according to the design and application, but a typical amount would be about one quarter of a teaspoon per hour. Generally, this is such a small amount that if the leaked fluid is a liquid, it tends to evaporate rather than pool, and therefore remains unnoticed.
  • one of the seal faces is configured to be axially movable, and an axial force is applied thereto during operation so as to press it toward the other seal face and thereby compensate for wear, axial thrust, thermal expansion, and/or any other mechanism that might compromise the gap between the seal faces.
  • the axial thrust can be applied by a pressurized process fluid, and/or by a mechanical loading that is provided by a spring, bellows, or other pressing mechanism. This applied axial force is opposed by a hydrodynamic pressure of the lubricating fluid within the gap, thereby creating an equilibrium that maintains the small but finite gap size.
  • the associated secondary seal So as to accommodate the axial movements of the axially movable seal face, it is necessary for the associated secondary seal to be axially adaptive, in that it must maintain the secondary seal between the seal face and its associated structure (housing or rotating shaft) as the seal face is axially moved.
  • Either of two types of axially adaptive secondary seal are typically used for this purpose, either a "pusher” secondary seal or a “non-pusher” secondary seal.
  • Pusher secondary seals are secondary seals for which the element forming the seal is axially mobile.
  • an O-ring is used to form a seal with a cylindrical element that is co-axial with the seal faces and is fixed to the housing or shaft, so that the O-ring is able to roll along the cylindrical element as the axially movable seal face undergoes axial movements.
  • These O-ring pusher seals respond well to elevated pressures, due to the elastomeric deformation of the O-ring, which increases the contact area of the seal when the applied pressure is increased.
  • Non-pusher seals are secondary seals for which the element that forms the seal remains fixed in its attachment to the housing or shaft, and accommodates the axial movements of the associated seal face by expanding or contracting.
  • an expandable, elastomeric gasket is sometimes used, whereas for high temperature applications a bellows is often used. In either case, the contact area of the seal does not typically increase with pressure for a non-pusher secondary seal.
  • a mechanical seal is necessarily subjected to both the temperature and pressure of the process fluid.
  • a secondary seal that includes a gasket and/or O-ring can limit the maximum temperature at which a mechanical seal can operate, due to temperature limitations of the elastomer.
  • Non-pusher secondary seals that use a metal bellows can withstand higher operating temperatures as compared to elastomer secondary seals, but metallic bellows seals are complex, expensive, difficult to install and remove, subject to metal fatigue, and are still sometimes not able to withstand the full range of temperatures that may be desirable for a given application.
  • a high temperature, high pressure secondary seal design is disclosed that is simple in design (at least compared to a metallic bellows seal), easy to install and remove, extends the operating temperature range of a mechanical seal beyond existing limits, and, in embodiments, facilitates axial movement of an associated seal face.
  • the novel secondary seal design includes an annular sealing gasket and a backing plate that surround an underlying cylindrical sealing surface, which can be the outer surface of the rotating shaft, or of a collar that surrounds the rotating shaft and is fixed to either the shaft or to the housing.
  • all three of these elements are made of the same metallic material, so that effects of expansion and contraction with temperature are minimized.
  • the metallic material is Alloy 718 or another "super alloy" that maintains its strength at high temperatures.
  • the sealing gasket is configured to press radially inward so as to form a radial seal with the sealing surface, while also pressing axially against the backing plate to form an axial seal therewith.
  • the backing plate in turn, is either unitary with the associated seal face, permanently bonded to the seal face, or is otherwise sealed to the seal face.
  • the sealing gasket is shaped as approximately one-half of a hollow ring, so that the cross section thereof is shaped approximately like a capital letter "C".
  • the sealing gasket is manufactured through a stamping process, whereby an initially flat, annular metal ring is pressed between two close tolerance forms to create the "C" cross-sectional shape. Accordingly, the sealing gasket is much simpler and less expensive to manufacture than a typical non-pusher, metallic bellows.
  • the curved portion of the C-shaped sealing gasket profile is directed toward a C-shaped groove provided in the backing plate, so that when axial pressure is applied, the gasket is pressed into the groove.
  • the groove in the backing plate ends before it reaches the underlying sealing surface, so that the radially innermost portion of the gasket is exposed. This allows the inner radius of the C-shaped sealing gasket to deform under pressure and form an enhanced seal against the sealing surface.
  • the wall of the sealing gasket has a constant thickness, which in embodiments is about 0,127 mm (.005 inches).
  • the inner diameter of the sealing gasket is slightly smaller than the outer diameter of the cylindrical sealing surface, for example between 0,0127 and 0,0254 mm (.0005 and .001 inches) smaller on the diameter, creating an initial interference fit (i.e. a press-fit) against the underlying sealing surface before pressure is applied for the first time.
  • the outer surface of the sealing gasket, the inner surface of the backing plate groove, and the underlying sealing surface are all prepared with a highly smooth finish.
  • the finish of all of these surfaces has an Ra of 0,41 ⁇ m (16 micro-inches) or less.
  • the backing plate or plate will have a groove with similar dimensions to that of the secondary sealing gasket. Specifically, the constant radius cross section of the gasket mentioned above will match the radius of the groove in the backing plate.
  • the radially outward diameter of the backing plate groove is slightly smaller than the outer diameter of the gasket, for example between 0,0254 and 0,0508 mm (.001 and .002 inches) smaller in diameter, so that the sealing gasket fits tightly in the groove.
  • a retaining ring or snap ring is used to retain the gasket within the groove of the backing plate during initial assembly of the disclosed secondary seal.
  • the inner diameter of the sealing gasket forms an interference fit with the outer diameter of the cylindrical sealing surface at ambient pressure and temperature.
  • the sealing gasket is pressurized against the groove provided in the backing ring, causing it to yield and conform to the exact shape of the groove.
  • the exposed inner diameter of the gasket is pressed downward, so that it deforms against the outer diameter of the cylindrical sealing surface and the region of contact transitions from a line of contact to a surface of contact.
  • the area of the contact surface increases, improving the quality of the seal that prevents the pressurized fluid from passing between the inner diameter of the gasket and the outer diameter of the cylindrical surface.
  • the backing ring supports the remainder of the sealing gasket from full exposure to extreme pressures that could otherwise cause excessive yielding and even potential failure of the sealing gasket. Due to their smooth surface finishes, the seal face, backing plate, and sealing gasket are able to move axially along the cylindrical sealing surface during pressurized operation with limited opposition from frictional forces therebetween.
  • the deformed inner diameter of the gasket naturally retracts away from the underlying sealing surface, thereby creating a clearance fit to the cylindrical sealing surface, and allowing the sealing gasket, backing plate, and associated seal face to be easily removed and reinstalled during disassembly and maintenance.
  • the clearance of the clearance fit is between 0,0127 and 0,0254 mm (.0005 and .001 inches). Nevertheless, upon repressurizing during subsequent operation, the seal is improved and the leakage past the gasket, if any, is reduced in comparison to the initial operation.
  • the sealing gasket is manufactured via a stamping process, wherein a flat sheet-metal ring is pressed between two close-tolerance forms. This allows the mechanical seal faces to maintain the appropriate gap required for operation at all times. Additionally, in embodiments the sealing gasket, backing plate, and sealing surface are all composed of identical materials, so that thermal expansion is uniform throughout the secondary seal, thereby preventing any one of the components from unintentionally expanding or contracting away from or into one of the others. As a result, all established clearances and interferences are maintained regardless of temperature variations.
  • the present invention is a mechanical seal that includes a high pressure, high temperature compatible secondary seal.
  • the mechanical seal includes first and second seal faces sealed to corresponding first and second structures, one of the seal faces being a rotating seal face surrounding, fixed to, and coaxial with a rotating shaft, the other of the seal faces being a static seal face coaxial with the rotating seal face and fixed to a static housing, the seal faces having opposing sealing surfaces in close proximity to each other, thereby forming a non-contacting primary seal therebetween.
  • the first seal face is sealed to the first structure by a secondary seal that includes a cylindrical sealing surface surrounding and coaxial with the rotating shaft, and sealed to the first structure, an annular backing plate surrounding and coaxial with the rotating shaft and sealed to the first seal face, and an annular, metallic sealing gasket surrounding and coaxial with the sealing surface and proximal to the backing plate, the sealing gasket having an arcuate cross section that approximates a half-arc of a circle, curved axially toward the backing plate and terminated at an inner edge proximal to the sealing surface and an outer edge distal from the sealing surface.
  • An arcuate groove is formed in the backing plate proximal to the sealing gasket, the arcuate groove having an inner radius that is larger than the inner radius of the sealing gasket and a cross sectional curvature that is shallower than a curvature of the sealing gasket cross sectional shape, so that when the sealing gasket is axially pressed into the arcuate groove, it forms a seal with the backing plate while, at the same time, the inner edge of the sealing gasket is forced radially inward beyond the arcuate groove of the backing plate and against the sealing surface, thereby forming a seal with the sealing surface.
  • the backing plate, sealing gasket, and sealing surface are configured such that the inner edge of the sealing gasket initially forms a press-fit with the sealing surface before the sealing gasket is pressed into the arcuate groove.
  • the diameter of the inner edge of the sealing gasket can be between 0,0127 and 0,0254 mm (.0005 and .001 inches) smaller than the diameter of the sealing surface.
  • the backing plate, sealing gasket, and sealing surface can be configured such that, after the sealing gasket is pressed into the arcuate groove, the inner edge thereof forms a region of contact with the sealing surface that is shaped as a cylindrical band.
  • the backing plate, sealing gasket, and sealing surface can be configured such that, after the sealing gasket is forced by applied pressure into the arcuate groove, and subsequently said pressure is released, the inner edge of the sealing gasket is retracted from the sealing surface, forming a clearance fit gap therebetween.
  • the clearance fit gap is between 0,0127 and 0,0254 mm (.0005 and .001 inches) wide.
  • the sealing gasket can be made from Alloy 718.
  • the sealing surface, the backing plate, and the sealing gasket can all be made from the same metallic material. In some of these embodiments, the sealing surface, the backing plate, and the sealing gasket are all made from Alloy 718.
  • first seal face, backing plate, sealing gasket, and sealing surface can be axially movable relative to the second seal face.
  • the arcuate cross sectional shape of the sealing gasket can be uniform in thickness between the inner and outer edges thereof. In some of these embodiments, the uniform thickness of the sealing gasket is approximately 0,127 mm (0.005 inches).
  • an outer surface of the sealing gasket, an inner surface of the arcuate groove, and the sealing surface can be all prepared with a finish having an Ra of 0,41 ⁇ m (16 micro-inches) or less.
  • an outer edge of the arcuate groove can be between 0,0254 and 0,0508 mm (.001 and .002 inches) smaller in diameter than the outer edge of the sealing gasket.
  • the present invention is a high temperature, high pressure static seal design that extends the operating temperature range of a mechanical seal beyond existing limits, and which preferably facilitates axial movement of an associated seal face.
  • the novel seal design includes an annular sealing gasket 200 and a backing plate 102 that surround an underlying cylindrical sealing surface, which can be the outer surface of the rotating shaft 104 or of a collar 106 that surrounds the rotating shaft and is fixed to either the shaft 104 or to the housing 108.
  • the sealing surface is a collar 106 that surrounds the shaft 104, but is static and fixed to the housing 108.
  • the backing plate 102 is sealed to an associated seal face 110, which in Figs.
  • FIG. 1 and 2 is the static seal face 110, which forms a seal with the other seal face 112, which in Figs. 1 and 2 is the rotating seal face 112.
  • embodiments include a spring, bellows, or other mechanism that applied a longitudinal force 202 onto the backing plate 102 and associated seal face 110, so as to move the seal face 110 axially to compensate for wear, axial thrust, and other phenomena that might otherwise compromise the gap between the seal faces 110, 112.
  • the sealing gasket 200, backing plate 102, and sealing surface 106 are all made of the same metallic material, so as to permit operation at very high temperatures.
  • the metallic material is Alloy 718 or another "super alloy" that maintains its strength at high temperatures.
  • the sealing gasket 200 is configured to press radially inward so as to form a radial seal with the sealing surface 106, while also pressing axially against the backing plate 102 to form an axial seal therewith.
  • the backing plate 102 is either unitary with the associated seal face 110, permanently bonded to the seal face 110, or is otherwise sealed to the seal face 110.
  • the sealing gasket 200 is shaped as approximately one-half of a hollow ring, so that the cross section thereof is shaped approximately like a capital letter "C".
  • the curved portion of the C-shaped gasket profile is directed toward a C-shaped groove 300 provided in the backing plate 102, so that when axial pressure 202 is applied, the gasket 200 is pressed into the groove 300.
  • the groove 300 in the backing plate 102 ends before it reaches the underlying sealing surface 106, so that the radially innermost portion 302 of the gasket 200 is exposed. This allows the inner portion 302 of the C-shaped sealing gasket 200 to deform under pressure and form an enhanced seal against the sealing surface 106, as is illustrated in Fig. 4 .
  • the wall of the sealing gasket 200 has a constant thickness, which in embodiments is about 0,127 mm (.005 inches).
  • the inner diameter of the sealing gasket 200 is slightly smaller than the outer diameter of the cylindrical sealing surface 106, for example between 0,0127 and 0,0254 mm (.0005 and .001 inches) smaller on the diameter, creating an initial interference fit (i.e. a press-fit) against the underlying sealing surface 106, as illustrated in Fig. 3B , before pressure is applied for the first time.
  • the outer surface of the sealing gasket 200, the inner surface of the backing plate groove 300, and the underlying sealing surface 106 are all prepared with a highly smooth finish.
  • the finish of all of these surfaces has an Ra of 0,41 ⁇ m (16 micro-inches) or less.
  • the groove 300 in the backing plate 102 has similar dimensions to the sealing gasket 200.
  • the radially outward diameter of the backing plate groove 300 is slightly smaller than the outer diameter of the gasket 200, for example between 0,0254 and 0,0508 mm (.001 and .002 inches) smaller in diameter, so that the sealing gasket 200 fits tightly into the groove 300.
  • a retaining ring or snap ring is used to retain the gasket 200 within the groove 300 of the backing plate 102 during initial assembly of the disclosed secondary seal.
  • the inner diameter of the sealing gasket 200 forms an interference fit with the outer diameter of the cylindrical sealing surface 106 at ambient pressure and temperature, as illustrated in Fig. 3B .
  • the sealing gasket 200 is pressurized against the groove 300 provided in the backing plate, causing it to yield and conform to the exact shape of the groove 300.
  • the exposed inner diameter of the gasket 200 is pressed downward, so that it deforms against the outer diameter of the cylindrical sealing surface 106, and the region of contact 302 transitions from a line of contact to a surface of contact 302.
  • the initial shape of the sealing gasket 200 is indicated for comparison using dashed lines.
  • the area of the contact surface 302 increases, improving the quality of the seal that prevents the pressurized fluid from passing between the inner diameter of the gasket 200 and the outer diameter of the cylindrical surface 106.
  • the backing plate 102 supports the remainder of the sealing gasket 200 from full exposure to extreme pressures that could otherwise cause excessive yielding and even potential failure of the sealing gasket 200. Due to their smooth surface finishes, the seal face 110, backing plate 102, and sealing gasket 200 are able to move axially along the cylindrical sealing surface 106 during pressurized operation with limited opposition from frictional forces therebetween.
  • the deformed inner diameter 302 of the sealing gasket 200 naturally retracts away from the underlying sealing surface 106, thereby creating a clearance fit to the cylindrical sealing surface 106, and allowing the sealing gasket 200, backing plate 102 and associated seal face 110 to be easily removed and reinstalled during disassembly and maintenance.
  • the clearance 500 of the clearance fit is between 0,0127 and 0,0254 mm (.0005 and .001 inches).
  • Fig. 6 is a graph that presents breakout friction data for required axial load 202 to axially move the sealing gasket 200 in an embodiment ("C-seals”) 600 at various pressures, in comparison with O-ring 602 and J-seal technologies 604, 606.
  • Fig. 7 is a graph that presents typical average process fluid leakage through a secondary seal in embodiments of the present invention, where the "First Pressurization" curve 700 shows leakage during initial operation, wherein the sealing gasket 200 is initially deformed against the sealing surface 106, and the "Average after initial pressurization" curve 702 shows test averages during subsequent operation.
  • the sealing gasket 200 is manufactured via a stamping process, wherein a flat sheet-metal ring is pressed between two close-tolerance forms. This allows the mechanical seal faces 110, 112 to maintain the appropriate gap required for operation at all times. Additionally, in embodiments the sealing gasket 200, backing plate 106, and sealing surface 106 are all composed of identical materials, so that thermal expansion is uniform throughout the secondary seal, thereby preventing any one of the components 200, 102, 106 from unintentionally expanding or contracting away from or into one of the others. As a result, all established clearances and interferences are maintained regardless of temperature variations.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Gasket Seals (AREA)
  • Quick-Acting Or Multi-Walled Pipe Joints (AREA)

Claims (14)

  1. Garniture mécanique qui est configurée pour empêcher la fuite d'un fluide de traitement au-delà de la garniture mécanique, la garniture mécanique incluant une garniture secondaire compatible à haute pression et haute température qui est compatible avec des pressions élevées et des températures élevées du fluide de traitement, la garniture mécanique comprenant :
    des première et seconde faces de garniture (110, 112) scellées aux première et seconde structures correspondantes, l'une des faces de garniture (110, 112) étant une face de garniture rotative entourant, fixée à, et coaxiale avec un arbre tournant (104), l'autre des faces de garniture (110, 112) étant une face de garniture statique coaxiale avec la face de garniture rotative et fixée à un logement statique (108), les faces de garniture ayant des surfaces d'étanchéité opposées à proximité étroite l'une de l'autre, formant ainsi une garniture primaire sans contact entre elles ;
    la première face de garniture (110) étant scellée à la première structure par une garniture secondaire qui résiste à la fuite du fluide de traitement au-delà de la garniture secondaire, la garniture secondaire comprenant :
    une surface d'étanchéité cylindrique (106) entourant et coaxiale avec l'arbre tournant (104), et scellée à la première structure ;
    une plaque de fixation annulaire (102) entourant et coaxiale avec l'arbre tournant (104) et scellée à la première face de garniture ;
    un joint d'étanchéité métallique annulaire (200) entourant et coaxial avec la surface d'étanchéité (106) et proximal à la plaque de fixation (102), le joint d'étanchéité (200) ayant une section transversale arquée qui se rapproche d'un demi-arc de cercle, incurvée axialement vers la plaque de fixation (102) et se terminant au niveau d'un bord intérieur (302) proximal par rapport à la surface d'étanchéité (106) et d'un bord extérieur distal par rapport à la surface d'étanchéité (106) ; et
    une rainure arquée (300) formée dans la plaque de fixation (102) proximale au joint d'étanchéité (200), la rainure arquée (300) ayant un rayon intérieur qui est plus grand que le rayon intérieur du joint d'étanchéité (200), caractérisée en ce que la rainure arquée (300) a une courbure de section transversale qui est plus concave qu'une courbure de la forme en section transversale du joint d'étanchéité, de sorte que lorsque le joint d'étanchéité (200) est pressé axialement par le fluide de traitement dans la rainure arquée (300), elle forme une garniture avec la plaque de fixation (102) tandis que, en même temps, le bord intérieur (302) du joint d'étanchéité (200) est forcé radialement vers l'intérieur au-delà de la rainure arquée (300) de la plaque de fixation (102) et forme une surface de contact qui est pressée contre la surface d'étanchéité (106), formant ainsi une garniture avec la surface d'étanchéité (106), ladite surface de contact étant augmentée lorsque la pression du fluide de traitement est augmentée.
  2. Garniture mécanique selon la revendication 1, dans laquelle, dans la plaque de fixation (102), le joint d'étanchéité (200), et la surface d'étanchéité (106) sont configurés de façon à ce que le bord intérieur (302) du joint d'étanchéité (200) forme initialement un ajustement serré avec la surface d'étanchéité (106) avant que le joint d'étanchéité (200) ne soit pressé dans la rainure arquée (300).
  3. Garniture mécanique selon la revendication 2, dans laquelle, avant que le joint d'étanchéité (200) ne soit pressé dans la rainure arquée (300), le diamètre du bord intérieur (302) du joint d'étanchéité (200) est compris entre 0,0127 et 0,0254 mm (0,0005 et 0,001 pouces) plus petit que le diamètre de la surface d'étanchéité (106).
  4. Garniture mécanique selon l'une quelconque des revendications précédentes, dans laquelle la plaque de fixation (102), le joint d'étanchéité (200), et la surface d'étanchéité (106) sont configurés de façon à ce que, après que le joint d'étanchéité (200) a été pressé dans la rainure arquée (300), son bord intérieur (302) forme une région de contact avec la surface d'étanchéité (106) qui a la forme d'une bande cylindrique.
  5. Garniture mécanique selon l'une quelconque des revendications précédentes, dans laquelle la plaque de fixation (102), le joint d'étanchéité (200) et la surface d'étanchéité (106) sont configurés de façon à ce que, après que le joint d'étanchéité (200) a été forcé par une pression appliquée sur la rainure arquée (300), et qu'ensuite ladite pression a été relâchée, le bord intérieur (302) du joint d'étanchéité (200) soit rétracté de la surface d'étanchéité (106), formant un espace d'ajustement avec jeu (500) entre eux.
  6. Garniture mécanique selon la revendication 5, dans laquelle l'espace d'ajustement avec jeu (500) a une largeur comprise entre 0,0127 et 0,0254 mm (0,0005 et 0,001 pouces).
  7. Garniture mécanique selon l'une quelconque des revendications précédentes, dans laquelle le joint d'étanchéité (200) est réalisé en alliage 718.
  8. Garniture mécanique selon l'une quelconque des revendications précédentes, dans laquelle la surface d'étanchéité (106), la plaque de fixation (102), et le joint d'étanchéité (200) sont tous constitués du même matériau métallique.
  9. Garniture mécanique selon la revendication 8, dans laquelle la surface d'étanchéité (106), la plaque de fixation (102), et le joint d'étanchéité (200) sont tous réalisés en alliage 718.
  10. Garniture mécanique selon l'une quelconque des revendications précédentes, dans laquelle la première face de garniture (110), la plaque de fixation (102), le joint d'étanchéité (200), et la surface d'étanchéité (106) sont axialement mobiles par rapport à la seconde face de garniture (112).
  11. Garniture mécanique selon l'une quelconque des revendications précédentes, dans laquelle la forme en section transversale arquée du joint d'étanchéité (200) est d'épaisseur uniforme entre les bords intérieur et extérieur de celui-ci.
  12. Garniture mécanique selon la revendication 11, dans laquelle l'épaisseur uniforme du joint d'étanchéité (200) est d'environ 0,127 mm (0,005 pouces).
  13. Garniture mécanique selon l'une quelconque des revendications précédentes, dans laquelle une surface extérieure du joint d'étanchéité (200), une surface intérieure de la rainure arquée (300), et la surface d'étanchéité (106) sont toutes préparées avec un finissage ayant un Ra de 0,41 µm (16 micro-pouces) ou moins.
  14. Garniture mécanique selon l'une quelconque des revendications précédentes, dans laquelle un bord extérieur de la rainure arquée (300) est compris entre 0,0254 et 0,0508 mm (0,001 et 0,002 pouces) plus petit que le bord extérieur du joint d'étanchéité (200).
EP19819368.2A 2018-06-14 2019-05-30 Joint mécanique avec joint secondaire haute température et haute pression Active EP3807559B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US16/008,214 US10557554B2 (en) 2018-06-14 2018-06-14 Mechanical seal with high pressure high temperature secondary seal
PCT/US2019/034567 WO2019240957A1 (fr) 2018-06-14 2019-05-30 Joint mécanique avec joint secondaire haute température et haute pression

Publications (3)

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EP3807559A1 EP3807559A1 (fr) 2021-04-21
EP3807559A4 EP3807559A4 (fr) 2021-07-28
EP3807559B1 true EP3807559B1 (fr) 2023-01-04

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EP (1) EP3807559B1 (fr)
CN (1) CN112334689B (fr)
CA (1) CA3103437C (fr)
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WO (1) WO2019240957A1 (fr)

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CN218177492U (zh) * 2022-03-23 2022-12-30 上海荣威塑胶工业有限公司 内置电动气泵

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MX2020013616A (es) 2021-05-27
WO2019240957A1 (fr) 2019-12-19
CA3103437A1 (fr) 2019-12-19
CN112334689B (zh) 2023-07-07
EP3807559A4 (fr) 2021-07-28
US10557554B2 (en) 2020-02-11
CN112334689A (zh) 2021-02-05
EP3807559A1 (fr) 2021-04-21
CA3103437C (fr) 2021-05-18
US20190383398A1 (en) 2019-12-19

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